Power tong head and assembly



Dec. 16, 1969 mc ET AL 3,483,774

POWER TONG HEAD AND ASSEMBLY 9 Sheets-Sheet 1 Filed Oct. 17, 1967 M: W m

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POWER TONG HEAD AND ASSEMBLY v Filed 001:. 1'7, 1967 9 Sheets-Sheet 2 J'N VENTOIQS.

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Dec. 16, 1969 J. L. DICKMANN ET AL 3,483,774

POWER TONG HEAD AND ASSEMBLY 9 Sheets-Sheet 3 Filed Oct. 17, 1967 Jvvewroes.

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POWER TONG HEAD AND ASSEMBLY Filed Ct. 17, 1967 9 Sheets-Sheet 4 12v YEN 7'02 5.

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- POWER TONG HEAD AND'ASSEMBLY Filed Oct. 17, 1967 Q-Sheets-Sheet 5 IN vawroes.

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POWER TONG HEAD AND ASSEMBLY 9 Sheets-Sheet 6 Filed Oct. 17, 1967 & M e E VK -6 Q aa M M WW 5 H a a W. Ivy 5 4 U M A 0 5 4/ 4. M J Z WH Dec. 16, 1969 J DlCKMANN ET AL 3,483,774

POWER TONG HEAD AND ASSEMBLY Filed Oct. 17, 1967 9 Sheets-Sheet 7 6'5 Ifra. E0 69 Jivvew 7-025.

JOHN Z. O/CKMA/I/A/ HOW/460 fiFZ/(L Dec. 16, 1969 J. L. DICKMANN ET AL 3,483,774

POWER TONG HEAD AND ASSEMBLY I l 9 Sheets-Shed 8 Filed Oct. 17, 1967 Jive/V7025. OHN L O/CCMA/VA/ HOW/4,60 5.

Dec. 16, 1969 J. L. DICKMANN ETAL 3,483,774

POWER TONG HEAD AND ASSEMBLY 9 Sheets-Sheet 9 Filed Oct. 17, 1967 u m w W \SQJ y wmfi wm\ m w 7 Wk M e y NA 5 MM H WN M nitc States Patent 3,483,774 POWER TONG HEAD AND ASSEMBLY John L. Dickmann, Whittier, and Howard S. Flick, Long Beach, Calif., assignors to Byron Jackson Inc., Long Beach, Calif., a corporation of Delaware Filed Oct. 17, 1967, Ser. No. 675,843 Int. Cl. B!) 21/00; B23p 19/06 US. Cl. 81-57 15 Claims ABSTRACT OF THE DISCLOSURE A power tong in which the rotary head has opposed jaws slidably mounted in jaw guides and shiftable radially outwardly by springs and radially inwardly by cam surfaces and cam followers, the cam surfaces being compound so as to move the jaws inwardly upon rotation of an outer drive ring in either direction relative to an inner jaw supporting ring.

CROSS REFERENCES TO RELATED APPLICATIONS BACKGROUND OF THE INVENTION Field of the invention The present invention relates to power tongs, or Wrenches, of the general type employed for the purpose of making up or breaking out the joints of pipe or rods as lengths of such pipe or rods are connected in or disconnected from a string being run into or retrieved from a well, such as an oil or gas well.

More particularly the invention involves an improved tong head adapted to be operated by a power system so as to grip or engage the couplings of the length of pipe or rods, hereinafter for simplicity referred to generically as pipe, to rotate the same, while the adjacent pipe is held stationary by a back-up tong or wrench which may be for expediency made a part of the power tong assembly or may be a separate tong or wrench. By driving the gripped pipe in one direction or the other the joints between the pipe stands or lengths may be made up or broken out.

Such tongs must be durable and effective in operation in order to facilitate the running in of long strings of t pipe or the removal of such long strings of pipe from a well, such pipe strings being thousands of feet in length and being composed of short stands or lengths of pipe which may be conveniently handled in a derrick. Moreover, the joints, particularly old joints, may require the application of a number of thousands of foot pounds of torque when the joints are being broken out. Thus, a problem exists in respect of deformation of the joints due to the application of high compressive forces thereto to enable gripping of the pipe in dies driven by the power system.

Since the pipe is run or pulled by a hoist system of substantial strength on speed of operation, the jaw system which carries the gripping dies should be operable in such a fashion as to be fully retracted or out of the way when disengaged from the pipe so as to allow longitudinal movement of the pipe through the tong head without iii) requiring that the tong be shifted laterally out of the way, thus enabling more rapid running or pulling of pipe strings, and yet the jaws should properly engage and centralize the pipe upon engagement therewith.

Summary of the invention Accordingly, among the objects of the invention is the provision of a power tong assembly having a tong head comprising the charteristic outer drive ring and a relatively rotatable inner ring including retractable pipe gripping jaws which are shiftable along a line extended diametrically of the pipe opening in the head, said jaws having opposing die elements which will engage and center the pipe upon engagement therewith so as to efiiciently transmit torque to the pipe upon operation of the tong in either direction.

Another object is to provide a power tong assembly including a head having retractable jaws, as aforesaid, each jaw having die carriers which may be easily changed to enable handling of the pipe efficiently over a wide range of pipe sizes.

Still another object is to provide a pipe tong assembly having a tong head in which radially movable jaws are provided with cam followers and are slidably supported in an inner ring assembly and spring loaded away from one another, the outer ring being composed of a large bull gear revolvable in either direction by power means and having opposite cams operable upon the followers of the respective jaws to force the jaws toward one another upon rotation of the bull gear.

Still another object of the invention is to provide a tong assembly including a tong head which is a selfcontained unit adaptable to various power mechanisms.

Other objects and advantages of the invention will be hereinafter described or will become apparent to those skilled in the art, and the novel features of the invention will be defined in the appended claims.

BRIEF DESCRIPTION OF THE DRAIVINGS FIG. 1 is a view in perspective illustrating a tong assembly made in accordance with the invention;

FIG. 2 is a fragmentary top plan view of the assembly of FIG. 1, showing the tong head and transmission subassemblies;

FIG. 3a is a fragmentary longitudinal section through the tong assembly as taken on the line 33 of FIG. 2, and showing the tong head;

FIG. 3b is a continuation of FIG. 3a, showing the power transmission;

FIG. 4 is a horizontal section taken on the line 44 of FIG. 3a;

FIG. 5 is a transverse section taken on the line 5-5 of FIG. 4;

FIG. 6 is a fragementary view partly in section and partly in plan showing the reverse stop mechanism of the tong head;

FIG. 7 is a view taken on the line 7--7 of FIG. 6;

FIG. 8 is a horizontal sectional view as taken on the line 8-8 of FIG. 3b;

FIG. 9 is a horizontal sectional view as taken on the line 99 of FIG. 312;

FIG. 10 is a horizontal sectional view as taken on the line 10-10 of FIG. 312;

FIG. 11 is a fragmentary view in side elevation showing the manifold and control means for the motors, the case being broken away;

FIG. 12 is a view in rear end elevation of the structure of FIG. 11;

FIG. 13 is a view in section as taken on the line 1313 of FIG. 12, showing the compound control rock shaft assembly;

3 FIG. 14 is a view in section on the line 1414 of FIG. 12;

FIG. 15 is a view in section on the line 15-15 of FIG. 12;

FIG. 16 is a fragmentary view in side elevation showing the connection of the actuator lever to the operating means for the motor control valves;

FIG. 17 is a fragmentary view in section as taken on the line 1717 of FIG. 16; and

FIG. 18 is a fragmentary view in section as taken on the line 1818 of FIG. 17.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring first to FIGS. 1 and 2, a tong assembly embodying the invention will be seen to comprise three separate and distinct subassemblies comprising a pipe gripping or tong head assembly 1 adapted to grip a joint and rotate the same relative to another joint, which joints together compose a threaded connection or joint between stands of well tubing or pipe or sucker rods, all of which are generically referred to herein as pipe, an illustrative length of which is generally illustrated at 2 and includes a joint or coupling 3. Also included in the tong assembly is a power transmission subassembly generally denoted at 4 which contains drive means for elfecting rotation of the pipe gripping mechanism included in the tong head. Included in the power transmission subassembly is a plurality of motors, designated M1 and M2 in the illustrative embodiment, these motors, as will hereinafter be more fully described, being adapted to drive the transmission mechanism at a relatively high speed and low torque, on the one hand, and at a relatively low speed and high torque, on the other hand, and in opposite directions. Further, the composite assembly includes a control subassembly generally denoted at 5 whereby an operator of the tong, in the making up and breaking out of pipe or rod joints, will be enabled to cause the motor M2 to operate in either selected direction, while motor M1 remains idle so as to drive the pipe gripping mechanism at a relatively high rate of speed but at low torque, such as would be desirable when a joint is being initially made up and offers little resistance, such relatively high speed initial making up of the joint being generally referred to in the field as spinning. Thereafter it is desired that the joint be finally made up by the application of relatively high torque forces which the tong operator may accomplish by causing, through the manipulation of the control mechanism 5, the simultaneous operation of motors M1 and M2 in such a manner that the transmission mechanism will impart to the gripping mechanism high torque loads but at low speed, so as to shoulder or finally tighten up the joint. Alternatively, in the breaking out of a joint the gripping mechanism must impose high torque loads on the joint in order to initiate its rotation so that the control mechanism 5 is adapted to enable the reverse rotation of both of the motors M1 and M2 in such a manner as to cause high torque, low speed rotation of the pipe gripping mechanism to initially break out the joint, and, thereafter, the control mechanism may be manipulated to allow the motor M1 to idle as the motor M2 continues to drive the pipe gripping mechanism at a relatively high speed under the reduced torque requirements for spinning the joint out.

Referring now more specifically to the tong head assembly 1, as best illustrated in FIGS. 3a through 7, it will be seen that this subassembly comprises a split case including an upper case section 6 and a lower case section 7 joined on substantially a median plane by suitable fasteners 8; the case defines a generally circular head end 9 which houses a pipe gripping mechanism generally denoted at G; and in a longitudinally extended, substantially rectangular case section 10 there is housed gear mechanism or other suitable drive means, to be hereinafter described, for effecting rotation of the pipe gripping means G.

The pipe gripping means G comprises an outer ring 11 which is of generally U-shape cross-section providing an inwardly opening channel 12. The outer ring 11 is provided about its outer periphery with drive elements in a specifically illustrated form of gear teeth 13, so that the outer ring may be said to constitute a bull gear. Suitable bearing means are provided for supporting the outer ring 11 for revolution within the case section 9, such bearing means being shown as ball bearings 14 engaging in annular races 15 formed about the outer wall of the outer ring 11 and riding in races 16 provided within the case section 9. Suitable seal rings 17 may be provided between the case and a confronting portion of the outer ring 11 to prevent the entry of Well fluids or other materials into the case section 9 which might otherwise cause damage to the drive mechanism for the outer ring 11.

As best seen in FIG. 4, the outer ring 11 is provided with diametrically opposing compound cam sections, each including a central low region 18 and oppositely extending rising surfaces 19, these rising surfaces each being formed on an arc of progressively decreasing radii from said low region, and the rising surfaces of the opposing cam sections, in the illustrative embodiment, meeting one another at a diametrical plane at right angles to a diametrical plane of the outer ring 11 extending through the low regions 18 of the camming sections. This is to say that the portion of the rising cam surfaces 19 adjacent the low region 18 of the cam sections is formed on an are having a greater radius than an intermediate portion of the rising surfaces, and the intermediate portions of the rising surfaces are struck on an arc of greater radius than the portions of the rising surfaces nearest the end thereof remote from the low region.

Revolvably disposed within the outer ring 11 is what may be typified as the inner ring assembly, generally denoted at 20. Included in the inner ring assembly 20 (see FIGS. 3a, 4 and 5) is a pair of guide members, including an upper tubular guide 21 and a lower tubular guide 22. respectively having diametrically opposed, axially extended arms 23 and 24 which confront one another substantially at the mid plane of the tong head. These arms define therebetween lateral openings 25 of rectangular form and in diametrically opposed relation, these openings leading into the central axially extended opening through the composite guides 21 and 22, this latter central opening constituting an opening through which pipe or rods may be extended as they are being run into or ulled from a well by the usual hoist equipment in the derrick, all as is well known in the art; and in order to facilitate movement of couplings into and through the central opening of the guides, the upper guide 21 has a beveled or fiared wall 26, and the lower guide 22 has a beveled or flared wall 27.

Means are provided for joining the guide sections in assembled relation, as well as for supporting in the lateral openings 25 a pair of hollow jaw guides 23, 28. Such means, in the illustrative embodiment, includes a pair of jaw guide clamps or plates 29, 29 which, as best seen in FIGS. 4 and 5, have a series of axially spaced grooves 30 and ribs 31 formed in an arcuate inner mid section of the plates 29 complementally with grooves 32 and ribs 33 formed in the arms 23 and 24 of the respective upper and lower guides 21 and 22. It will be understood that these complemental and co-engaged ribs and grooves not only support the jaw guide clamps or plates 29 on the composite guides, but also that these ribs and grooves hold the composite guide assembly together in the relationship as shown in FIG. 3a.

The jaw guides 28 constitute box-like hollow members having side walls 34 provided with vertically extended external ribs 35 disposed in complemental vertical grooves 36 in the plates 29, suitable fastening means, such as screws 37, extending through the jaw guide walls 34 and into the clamp plates 29 so as to maintain all of the components, including the guides 21 and 22, the clamp plates 29, and the jaw guides 28, in an integrated assembly, with the jaw guides 28 extending radially outwardly into the channel 12 formed in the outer ring 11, as reviously described. This integrated assembly, con stituting the inner ring 20, is adapted to be supported for rotation relative to the outer ring 11, and, illustratively, it will be noted that the upper guide 21 has an outwardly extended flange 38 which supports the inner ring assembly on the upper outer wall of the outer ring 11, while the corresponding flange 39 of the guide 22 is slightly downwardly spaced from the corresponding lower outer wall of the outer ring 11. Thus, the inner ring is disposed within the outer ring 11 for relative rotation thereof.

The gripping mechanism G further includes a pair of jaws 4t 40 slidably disposed within the jaw guides 28 for radial movement into and out of the central opening through the guides 21 and 22. Included in each of the jaws 40 is a die carrier 41 adapted to be removably retained in a seat 42 as by means of fasteners 43. At the outer end of each of the jaws 40 cam follower means in the form of a roller 44 supported on a vertical shaft 45 are provided in each jaw, these rollers 44 being engageable with the cam sections previously described in the outer ring 11. Means are provided for normally biasing the jaws 40 outwardly to cause engagement of the rollers 44 with the cam sections, and such means (see FIG. 4) may comprise a suitable number of coiled compression springs 46 seated at one end in bores 47 in the side walls 34 of the jaw guides and abutting at their other ends against a foot provided on an L-shaped spring seat 48, a leg of which is disposed in a slot 49 in the jaw 40 and retained therein as by a pin 50.

It will now be apparent that with the structure as thusfar described, relative revolution of the outer ring 11 about the inner ring 20 will cause movement of the cam sections relative to the followers 44, so that the latter will be cammed inwardly by one of the rising surface 19, depending upon the direction of rotation of the outer ring 11. In order to assure that such relative rotation will occur when the outer ring 11 is driven, brake means are provided for applying a drag to the inner ring 2t). Illustratively, such brake means comprises a brake band 51 having friction material 52 thereon and engageably with the outer peripheral surface of the flange 39 of the lower guide 22, the brake band 51 being retained against downward displacement from the flange 39 by means of a bottom plate 53 secured to the case section 7 as by fasteners 54 and extending into underlying relation to the brake band. In order to anchor the brake band against rotation with the inner ring 20, anchor means are provided and, in the illustrative embodiment, such anchor means comprise ears 55 formed on the extremities of the brake band and extending downwardly through a slot 56 in the plate 53. These ears 55 are joined together in a suitable state of tension adjustment about the inner ring flange 39 by means of a suitable adjuster screw 57; and it will be understood that the ears 55 respectively constitute anchoring abutments engageable with the extremities of the slot 56 to anchor the brake band.

In order to grip a joint disposed within the gripping means G when the jaws 40 are moved toward one another responsive to relative rotation between the outer ring 11 and the inner ring 20, the die holders 41, previously referred to as constituting a part of the jaws 40, are provided with suitable die means, including a pair of similar dies 58, each having along vertical edges thereof teeth 59 adapted to bite into the coupling on engagement therewith. These dies 58 are disposed in dovetail slots 58a extending vertically in the die carriers 41 and generally disposed at an angle relative to the diametrical lines extending across the central opening through the guides, so that the dies will engage with one or another of the teeth 59 a substantial range of joint diameters without requiring changing of the dies 58 or the die carriers 41. The vertically toothed dies 58 herein illustrated may be, moreover, replaced by arcuate toothed dies which more particularly are designed to fit with a particular joint diameter, as is well known in the art.

Following the gripping and rotation of a joint part by the gripping means G, it is desired that the gripping means be released from the joint part in response to reversal of the direction of rotation of the outer ring 11 to cause return movement of the followers 44 to the low regions 18 of the camming sections within the outer ring. Means are provided to prevent the continued relative rotation between the outer ring 11 and the inner ring 20 to prevent the gripping means from again being actuated into gripping engagement with the joint part as a result of reversal of the rotation. Such means is best illustrated in FIGS. 3a, 6 and 7 wherein it will be noted that a flange 60 is provided in overlying relation to the seal means 17, this flange 60 being secured to the upper wall of the outer ring 11 as by a suitable number of fasteners (not shown). Within the flange 60 there is provided an annular seat 62 in which is rotatably disposed a ring 63. At at least one location about the ring 63 is a downwardly extended lug 64 which extends into an upwardly opening slot 65 in a sliding block 66 having upstanding end lugs 67, 67. Coiled springs 68, 68 are interposed between the opposing end lugs 67 and the intermediate lug 64 of the ring 63, and means are provided for causing rotation of the ring 63 relative to the flange 60, for example, a pair of outwardly extended lever arms 69 projecting outwardly from the ring 63 for manual engagement. The relative angular position of the ring 63 is adapted to be adjusted within the limits of elongated arcuate slots 70 provided in the flange 60, locking screws 71 carried by the ring 63 extending through the slots 7% and into threaded engagement with the outer ring 11. It is now apparent that the outer ring 11, when rotating, carries with it the flange 6t and the ring 63, and, in order to prevent reverse actuation of the gripping means G into engagement with the joint part as aforementioned, stop elements are provided on the guide 21, these stop elements being in the form of rollers 72 mounted in the outer peripheral wall of the flange 38 of guide 21 in angularly spaced relation and selectively engageable by floating rollers 73, one of which is adapted to be cammed inwardly for engagement with one of the rollers 72, depending upon the relative adjusted position of the ring 63. As best seen in FIG. 6, these floating rollers 73 are adapted to be cammed inwardly by wedge surfaces 74 at the opposite ends of the floating block 66, these wedge surfaces 74 being opposed by wedge surfaces 75 formed in the inner periphery of the flange 60. As will now be apparent, the floating block 66 is biased by one of the springs 68, depending upon the position of ring 63, to a position at which the opposing wedge surfaces 74 and 75 will hold one of the rollers 73 in a radially inwardly displaced position for engagement with one of the rollers 72. In FIG. 6 it will be noted that the outer ring assembly is free for counterclockwise rotation relaive to the inner ring guide 21, but clockwise rotation will be prevented. Thus, the tong head assembly may be employed to turn a joint part in a counterclockwise direction, but the gripping means G will be prevented from reverse actuation when the outer ring 11 is rotated in the reverse direction, so that the inner ring 20 will be caused to rotate along with the outer ring 11 when the followers 44 are at the low regions 18 of the camming sections.

As seen in FIGS. 1, 2, 3a and 3b, the tong head case sections 6 and 7 extend outwardly from the generally circular head end 9 thereof so as to form the box-like section 16 of the case in which is disposed the illustrative gearing by which the bull gear-like outer ring 11 is to be driven. This gearing includes a large ring gear 76 having a hub 77 journalled in bearings 78 supported between the case sections 6 and '7. The ring gear 76 is in mesh with a pinion 79 which is journalled in bearings 80 mounted in the case sections 6 and 7 and adapted to be driven by a lower splined section 81 of a short splined shaft 82 which extends through an opening 83 in the upper case section 6, and, more particularly, through a horizontally extended wall 6a thereof which constitutes a portion of means, including the wall 6a, for connecting the tong head case to the power transmission mechanism 4 now to be described.

This transmission means or section 4 of the assembly also comprises a longitudinally split case having an upper case section 85 and a lower case section 86 having a wall 86a mating with the wall 6a of head assembly 1 and suitably joined thereto as by fasteners 87, this wall 86a having an opening 88 aligned with opening 83 in head case wall 6a. Journalled in the opening 88 is the hub 89 of a large ring gear 90 constituting the driven gear of the gearing means of the transmission. The short splined shaft 82 previously described has a splined end 91 engaged in the hub 89 so that power is transmitted from the gear 90 to the head gearing 79, '76, 11.

The motors M1 and M2 previously referred to are adapted to drive the ring gear 90, and, accordingly, these motors are mounted beneath a portion of the transmis sion case which extends rearwardly from the head case. The motor M1 is preferably a hydraulic or other reversible fluid motor having an output shaft 92 on which is a pinion 93 engaged with ring gear 90 within the transmission case, so as to drive the ring gear 90 in opposite directions at a speed dependent upon the gear ratio and the flow of fluid through the motor M1.

Motor M2 is also mounted beneath the transmission case adjacent motor M1 and has an output shaft 94 adapted to drive the ring gear 90 in opposite directions through double acting, self-energizing, overrunning clutch means C interposed between the drive pinion 95 and the motor shaft 94. This clutch means is illustrated in FIGS. 3b and 8l0 as including a power input or drive part 96 s lined to the motor shaft 94 and a power output or driven part 97 journalled in the transmission case and integral with, or otherwise made a part of, the pinion 95.

More particularly, this overrunning clutch means includes camming surfaces 98 arranged in equidistantly spaced relation about the drive part 96 and engageable with a like number of rollers 99 to urge the latter outwardly into driving relation with the inner periphery of a wall 100 formed as a part of the driven clutch part 97 (see FIG. 8). These rollers 99 are supported in a carrier ring 101 which also supports a plurality of equidistantly spaced additional rollers or balls 102 engaged with the camming surfaces 98. These balls 102 are normally biased inwardly into engagement with the camming surface 98 by a resilient spring ring 103 disposed about the balls; and this spring ring functions to normally tend to centralize the balls 102 with respect to the camming surfaces 98, thereby also centralizing the rollers 99 with respect to the surfaces 98. Fixed drag brake means are provided so that when the drive part 96 is rotated in either direction relative to the driven part 97, the clutch will be engaged. This brake means comprises a cuplike brake drum 104 supported within the case section 86 between a pair of snap rings 105. Within the brake drum 104 is a discontinuous drag ring 106, the ends of which are spaced apart (see (FIG. The roller carrier 101 has an outward projection or abutment 107 extending into the space between the ends of the drag ring 106. When the drive part 96 is rotated, the camming surfaces 98 will force the balls 102 outwardly from their centralizing position transmitting the rotation to the roller carrier 101 until the pin 107, just referred to, engages one of the drag ring ends, depending upon the direction of rotation, whereupon further rotation of the roller carrier 101 will be resisted by frictional engagement of the drag ring 106 3 in the brake drum 104, and thus the rollers 99 will be forceably cammed outwardly into engagement with the wall of the driven part 97. Rotation of the brake drum 104 along with the drag ring 106 is prevented by provision of a suitable stop, such as a pin 108, engaging the drum 104 and fixed in the case 86.

From the foregoing, it will now be understood that in operation the motor M1 may drive the ring gear 90 in either direction and, unless the motor M2 is also operating to drive the clutch drive part 96, the clutch driven part 97 will idle along with the ring gear 90; however. when the motor M2 is operated to cause rotation of the clutch drive part 96, then both of the motors will be effective to drive the ring gear 90 in either direction, such selective operation of the motors M1 and M2 is adapted to be controlled by control means for the flow of fluid t0 the respective motors from a source, as will now be described.

The control section 5 of the tong assembly, as generally illustrated in FIG. 1, includes a cover or case 109 which, as seen in FIG. 11, is adapted to be connected to the rear end of the transmission subassembly 4 on a supporting bracket 110 having ears 111 secured by fasteners 112 to the transmission case. Within the cover 109 and supported on the bracket 110, as at 113, is a fluid manifold and valve assembly generally denoted at V, whereby to control the flow of power fluid from a source (not shown) to the respective motors M1 and M2. Schematically illustrated in the valve and manifold assembly V, as seen in FIG. 12, is a first valve means V1 and a second valve means V2. respectively adapted to control the flow of motor fluid to the motors M1 and M2 under the influence of operating means generally denoted at O, which operating means is operable by actuator means generally denoted at A. Accordingly, valve V1 is adapted to control the flow of fluid from the source leading into the manifold at an inlet 114 and leading from the manifold at an outlet 115 from the motor M1 in such a manner that fluid will flow from the inlet 114 through a valve passage 116 to motor M1 and from that motor through a conduit 117 and a valve passage 118 through the valve and to the outlet 115, so as to drive the motor M1, say in a left-hand direction, when the valve is in a first position. The valve V1 is operable when it is in a second position to cause a reversal of the direction of flow so that the motor M1 will be driven in the opposite or right-hand direction. Likewise, the valve V2 is adapted to control the flow of fluid through the motor M2 in reverse directions by causing the flow of fluid from the inlet 114 through a valve passage 119 and from the motor through a conduit 120 and thence a valve passage 121, whereby the motor M2 will rotate in a lefthand direction; and, when the valve V2 is adjusted to a second position, the flow of fluid will be reversed, causing the operation of the motor in a right-hand direction. It will be understood that the arrangement of the valves and the flow passages is merely illustrative and that any desired four-way valves or other valve means may be employed to accomplish the reversal of fluid flow through the two motors, but it is preferred that the operating means 0 be so constructed as to move the valve V1 to its first position or to its second position while the valve V2 remains closed, but, when it is desired, the valve V2 may be moved either simultaneously with, or after movement of, the valve V1 to its first and second positions.

This operating means comprises a rock shaft 122 rotatably mounted in transversely extended relation by a pair of arms 123 depending from the bracket 110. The rock shaft 122 is a hollow shaft within which is revolvably disposed a second rock shaft 124. As seen in FIGS. 13 and 14, the inner rock shaft 124 has a lever arm 125 connected thereto and extending laterally through an opening 126 in the hollow rock shaft 122, this opening 126 being extended angularly so as to provide clearance space between end walls 127 and 123 thereof. As seen in FIGS. 13 and 15, the inner rock shaft 124 also has a lever arm 129 projecting therefrom and through an opening 130 providing angularly spaced abutments 131 and 132 engageable with the lever arm in a manner hereinafter to be described. Carried by the lever arm 125 is a valve operating linkage means 133 adapted to be connected to the valve V1 so as to move the latter between its first and second positions from its off position; and connected to the lever arm 129 is linkage means 134 adapted to be connected to the valve V2 to cause its operation between its first and second positions from its off position.

The actuating means A for the operating means 0, just described, is located at one end of the rock shafts 122 and 124, but preferably at each end of said rock shafts, so as to enable operation of the long assembly from either side thereof. As best seen in FIGS. 12, 16 and 17, the actuator means comprises a lever 135, the lever being pivotally supported on pins 136 which are carried by a member 137 which is connected to the hollow rock shaft 122, the pins 136 extending into the hollow rock shaft so as to effect rotation of the latter when the lever 135 is moved between a normal position in either direction. The rock shaft 124 extends endwise from the hollow shaft 122 and has secured to its outer end a lever 138 having an arm extending lengthwise of the lever 135 between upper and lower walls 139 and 140 of the lever 135. Between these walls 139 and 140 are camming means generally denoted at 141 and including an upper wedge surface 142 and a lower wedge surface 143 defining there between a central slots 144. These wedge surfaces and slot are adapted to cooperate with an end 145 on the actuator lever 138 only when the lever 135 is pivoted to a laterally displaced outer position as shown in broken lines in FIG. 17, so that when the lever 135 is in its normal position, shown in full lines in FIG. 17, and is moved either upwardly or downwardly, it will effect corresponding rotative movement of the hollow rock shaft 122; but when the lever 135 is pivoted about pins 136 to the angular position shown in broken lines in FIG. 17, the end 145 of lever 138 will be engaged in the slot 144 within lever 135 so that the two levers will move simultaneously, thereby effecting simultaneous rocking movement of the hollow rock shaft 122 and the internal rock shaft 124. Thus it will be understood that the actuator lever 135 is effective to cause either movement of the outer rock shaft 122 alone, or together with the inner rock shaft 124, in opposite directions so as to effect either the operation of valve V2 upon abutment of either of the abutments 131 and 132 with the lever 129 or the simultaneous actuation of valve V1.

In addition, it will also be noted that when the outer rock shaft 122 is rotated in either direction so as to effect operation of valve V1, the spaced end Walls 127 and 128 of the opening 126, through which the operating lever 125 for valve V2 projects, will allow the rock shaft 122 to move to a first position without operating valve V2. Thereafter, depending upon the direction of movement of the actuator lever 135, one of the end walls 127 or 128 just referred to will engage the valve operating lever 125 to cause it to move in a corresponding direction so as to operate the valve V2 when the actuator lever 135 is in a second position. Thus, by the simple manipulation of the actuator lever 135, the tong may be driven at a high speed and low torque through the operation of the valve V1 upon movement of the lever 135 to a first position; upon movement of the lever 135 in the same direction to a second position, the valve V2 will be operated to cause operation of motor M1 which, through the clutch means previously described, will now Work with motor M2 so that the tong will be driven at a lower speed and higher torque, as would be desirable when making up a joint. However, when breaking out a joint, and it is desired that the tong be first operated at low speed and high torque, the actuator lever 135 may be pivoted about pins 136 to effect co-engagement of the lever 138 in the slot 144 of the actuator lever so that, when the lever is pivoted to actuate the valve mechanism, both valves V1 and V2 will be initially opened. To initiate operation of the tong, and when the joint has been broken out, the lever'135 may be moved inwardly to the full line position of FIG. 17 so that the valve V2 will close, thereby allowing the tong to operate at high speed and low torque to spin out the joint.

While the specific details of an illustrative embodiment of the invention have been herein shown and described, changes and alterations may be made Without departing from the spirit of the invention.

We claim:

1. In a power tong assembly for making up and breaking out joints of pipe, rod, and the like, and comprising: a supporting frame structure, reversible power transmission means carried by said frame structure, and pipe gripping means also carried by said frame structure and operable by said power means to grip and rotate a threaded joint part relative to another threaded joint part, whereby to make up and break out a joint composed of said joint parts, the improvement wherein said pipe gripping means comprises an outer ring having means for driving engagement with said transmission means, an inner ring revolvable within said outer ring, said inner ring having an opening axially thereof for reception of one of of said joint parts, a pair of jaws disposed in opposed relation at opposite sides of said opening, jawsupporting means shiftably mounting said jaws for movements toward and away from one another from retracted positions when said outer ring and said inner ring are in one relative angular position to projected positions for gripping said one joint part, and cam and follower means for shifting said jaws toward one another upon relative revolution of said outer ring and said inner ring in either direction from said relative angular position at which said jaws are retracted,

2. A power tong assembly as defined in claim 1, wherein said outer ring and said inner ring include stop means selectively operable to prevent relative revolution of said outer ring and said inner ring in one direction from said one relative angular position.

3. A power tong assembly as defined in claim 1, including means operable to hold said inner ring stationary during initial revolution of said outer ring to cause tight engagement of said jaws with said one of said joint parts, said outer ring and said inner ring thereafter revolving in unison to rotate said joint part.

4. A power tong assembly as defined in claim 1, wherein said cam means includes a pair of cam sections each having a central low region and oppositely extended rising surfaces, and said follower means includes followers engaged with the respective cam sections and engaging the respective low regions of said cam sections when said outer ring and said inner ring are in said one relative angular disposition.

5. A power tong assembly as defined in claim 1, wherein said cam means includes a pair of cam sections each having a central low region and oppositely extended rising surfaces, and said follower means includes followers engaged with the respective cam sections and engaging the respective low regions of said cam sections when said outer ring and said inner ring are in said one relative angular disposition, and including means normally biasing said jaw supporting means apart.

6. A power tong as defined in claim 1, wherein said cam means includes a pair of opposed cam sections within said outer ring, and said follower means includes roller elements engaged with the respective cam sections and carried by the respective jaws.

7. A power tong as defined in claim 6, wherein each of said cam sections includes a central low region and oppositely extended rising surfaces.

8. A power tong as defined in claim 6, wherein each of said cam sections includes a central low region and oppositely extended rising surfaces, said rising surfaces being on an arc of progressively decreasing radii from said low region.

9. A power tong as defined in claim 1, wherein said outer ring comprises a bull gear having an internal channel extending circumferentially and opening radially inwardly, said inner ring comprising a central support revolvably mounted within said bull gear and having said opening axially of said inner ring for reception of said joint part, said jaw-supporting means being carried by said central support and extending outwardly therefrom into said channel.

10. A power tong as defined in claim 1, wherein said outer ring comprises a bull gear having an internal channel extending circumferentially and opening radially inwardly, said inner ring comprising a central support revolvably mounted within said bull gear and having said opening axially of said inner ring for reception of said joint part, said jaw supporting means being carried by said central support and extending outwardly therefrom into said channel, said cam means comprising cam surfaces within said channel, and said follower means comprising rollers carried by said jaw-supporting means.

11. A power tong as defined in claim 1, wherein said inner ring comprises a central tubular guide having said opening axially of said inner ring for reception of said joint part, said jaw-suporting means including hollow jaw guides carried by said central guide and projecting radially therefrom, and said jaws being shiftably disposed in said jaw guides.

12. A power tong as defined in claim 1, wherein said inner ring comprises a central tubular guide having said opening axially of said inner ring for reception of said joint part, said jaw-supporting means including hollow jaw guides carried by said central guide and projecting radially therefrom, and said jaws being shiftably disposed in said jaw guides, said jaw guides and said jaws respectively having opposed spring seats and springs in said seats urging said jaws outwardly in said jaw guides from said central tubular guide.

13. A power tong as defined in claim 1, wherein said inner ring comprises a central tubular guide comprising axially spaced annular guide sections having diametrically spaced support arms extended axially therefrom, said jawsupporting means including a pair of plates spaced apart by said support arms, and hollow jaw guides carried between said plates and opening into said central tubular guide between said support arms, said jaws being shiftably disposed in said jaw guides.

14. A power tong as defined in claim 13, wherein said plates and said arms have means for interconnecting said guide sections.

15. A power tong as defined in claim 14, wherein at least one of said guide sections has a radial flange extending outwardly therefrom, and said inner ring includes a portion engaged by said flange for supporting said inner ring on said outer ring for relative revolution thereof.

References Cited UNlTED STATES PATENTS 1,700,291 1/1929 Johnston 173l64 2,639,894 5/1953 Smith 81-57 2,720,803 10/ 1955 Rice. 2,780,950 2/ 1957 Province. 2,878,026 3/1959 Pioch 29-240 2,923,192 2/ 1960 Montgomery. 3,165,325 1/1965 Goepfrich 173-163 K 3,241,864 3/1966 Shaffer 16685 X 3,272,266 9/1966 Kennard 173-164 3,380,323 4/1968 Campbell. 3,382,559 5/1968 Kopec 29-240 FOREIGN PATENTS 662,261 4/ 1963 Canada.

WAYNE A. MORSE, JR., Primary Examiner 

